Pneumatic tool having combined nut running and crimping mechanism

ABSTRACT

A nut running tool in which is combined nut running and nut crimping mechanism. The tool is operative to crimp all six sides of a standard hexagonal nut. A reversible rotary air motor drivingly connected with the mechanism is operable in one direction to cause the mechanism to drive the nut to a predetermined tightness, and is operable in an opposite direction to cause the mechanism to crimp the nut. In one embodiment, control means is selectively operable to determine the direction of rotation of the motor. In a second embodiment, control means is provided which is operable without further intervention of the operator to cause the mechanism to run through a first stage to set the nut, then responds automatically to setting of the nut to cause the mechanism to crimp the nut, and finally responds to the latter action to restore the tool to its normal condition.

United States Patent [1 1 Amtsberg et a1.

[ 1 July 24, 1973 PNEUMATIC TOOL HAVING COMBINED NUT RUNNING ANDCRIMPING MECHANISM [75] lnventors: Lester A. Amtsberg, Utica; William K.Wallace, Bameveld, both of N.Y.

[73] Assignee: Chicago Pneumatic Tool Company, New York, N.Y.

221 Filed: Mar. 8, 1971 21 Appl. No.: 121,867

[52] U.S. Cl 81/10, 72/453, 10/155 R [51] Int. Cl B25b 27/00 [58] Fieldof Search 81/10; 72/453, 452, 72/391; 29/200 B, 211 D; 10/155 R [56] 7References Cited UNITED STATES PATENTS 3,689,951 9/1972 Van Hecke et a181/10 3,646,837 3/1972 Reynolds 81/10 3,603,132 9/1971 Holmes.... 81/553,479,714 11/1969 Allsop 81/3 Primary Examiner-James L. Jones, Jr.Attorney-Stephen J. Rudy [57] ABSTRACT A nut running tool in which iscombined nut running and nut crimping mechanism. The tool is operativeto crimp all six sides of a standard hexagonal nut. A reversible rotaryair motor drivingly connected with the mechanism is operable in onedirection to cause the mechanism to drive the nut to a predeterminedtightness, and is operable in an opposite direction to cause themechanism to crimp the nut.

In one embodiment, control means is selectively operable to determinethe direction of rotation of the motor.

In a second embodiment, control means is provided which is operablewithout further intervention of the operator to cause the mechanism torun through a first stage to'set the nut, then responds automatically tosetting of the nut to cause the mechanism to crimp the nut, and finallyresponds to the latter action to restore the tool to its normalcondition.

12 Claims, 17 Drawing Figures PNEUMATIC TOOL HAVING COMBINED NUT RUNNINGAND CRIMPING MECHANISM BACKGROUND OF THE INVENTION This invention isconcerned with a pneumatically powered nut runner having crimpingmechanism incorporated therein.

A nut runner including nut crimping mechanism is known from U.S. Pat.No. 3,003,378. This known tool is of a hand powered type and resorts toan impacting action to effect crimping of the work.

The general objective of the present invention is to provide a fluidpower operated nut runner with mechanism for crimping by means of asqueeze action on all six sides of a standard nut after it has beentightened upon a stud to the required torque. The crimping effect on thenut is of advantage in that it distorts its internal threads so as tolock it to the stud and make its removal difficult. A crimped nut upon astud is particularly desirable in situations where the article carryingthe nut will be subject to continual shocks and vibration which mightotherwise tend to loosen the nut from the stud.

Incorporation of the crimping mechanism in the tool is of advantage inthat it avoids the necessity of resorting to separate and independenttools to effect the crimping action; and results in a tool of compactnature which is practical and efficient for the operations involved.

A feature of the invention isa combined mechanism in a nut running toolfor effecting both the nut running and crimping actions. As will beapparent hereinafter, one embodiment of the tool can be operatedselectively to provide only nut runup, or only nut runup-followed bycrimping of the runup nut, or only crimping of a nut which has beenrunup by another tool.

Another feature of the invention lies in a rotatable.

member carrying a group of pivotable jaw elements which provide twodistinctive operational functions, namely, to run up a standardhexagonal nut upon a bolt to predetermined seated condition, andsubsequently to crimp all sides of the nut into tight engagement withthe bolt.

Another feature lies in the association of a wedge with the pivotablejaw elements, the wedge being movable axially of the jaw elements with acamming action against tail ends of the jaw elements so as to forcelower jaw face portions angularly in the crimping action to penetratethe work nut. This arrangement provides a desirable mechanical advantageand other benefits in the crimping action which are not obtainable bythe mechanism known from U.S. Pat. No. 3,003,378; nor from U.S. Pat. No.3,421,562. In the latter patent, a female member is slidable over jawelements to effect a crimping action on a work nut.

A characteristic of each jaw element is a flat planar face at its lowerinner end area which defines the jaw. This jaw face serves to contributeto an effective nut engagement area to achieve desired nut runup andalso is ccoperuble in a crimping action angularly with a flat side ofthe work nut so as to compressively displace a triangular volume ofmetal. This structural arrangement is of decided advantage in that itdoes not allow the jaw to become locked or bound to the nut in thecrimping action; and the jaw may accordingly be readily released.

Another feature of the combined nut running and crimping mechanism isthat it is coupled to the motor so as to be responsive to rotation ofthe motor in one direction to run down the work and responsive torotation of the motor in an opposite direction to crimp the work.

Another feature of the invention is manually operable air flow controlmechanism which permits selective rotation of the motor in one directionor the other.

In a modified or automatically operating form of the invention, an airflow control system is provided which is initially actuable to cause rundown of the work to a predetermined degree of tightness; respondsautomatically to a predetermined tightening of the work to causecrimping of the work; and responds to termination of the latter actionto shut off air flow to the motor and to restore the tool to its normalcondition,

BRIEF DESCRIPTION OF THE DRAWING In the accompanying drawing:

FIG. 1 is a sectional view of a nut runner embodying the invention;

FIG. 2 is a section on line 22 of FIG. 1;

FIG. 3 is a section on line 3-3 of FIG. 1;

FIG. 4 is a section on line 4-4 of FIG. 1;

FIG. 5 is a detail view of the travel wedge;

FIG. 6 is a bottom end view of FIG. 5;

FIG. 7 is a detail showing the normal or open position of a jaw elementallowing reception of a work nut;

FIG. 8 is a detail showing the jaw element pivoted in crimping relationto the work nut;

FIG. 8a is an elevational view of the inner face of the element in FIG.8b;

FIG. 8b is a detail in side elevation of a jaw element;

FIG. 9 shows the handle of the tool as modified with a valve systemallowing the tool to pass automatically through a complete cycle ofoperation in which a nut is set and crimped; and

FIGS. 10-15 are sectional views taken respectively on the lines l0l0;ll-ll; 12--l2; 1313;'l414; and 15-15 of FIG. 9.

DESCRIPTION OF PREFERRED EMBODIMENT Reference is directed to theaccompanying drawings, and now especially to FIGS. 1-8b, wherein isshown a pneumatically powered tool having a general housing 10 whichincludes an angle head section 11 detachably coupled, as by a threadedconnection 12, with the front end of the housing. Supported in thehousing is a conventional air driven reversible motor 13 of a radiallyslidable vane type. An inlet passage 14 to the tool is connectible to anexternal source of air having a constant pressure. A throttle valve 15is manually operable to feed inlet air to a passage 16. A manuallyoperable reversing valve 17 in passage 16 normally directs the air flowto one area of the motor chamber to cause forward or clockwise rotationof the motor. In an actuated position, the reversing valve directs airflow to a reverse area of the motor chamber to cause reverse orcounterclockwise rotation of the motor.

Rotation of the motor is transmitted through conventional reductiongearing, generally indicated at 18, and

through a splined driving connection 19 to a spindle 21. The spindleextends axially into one arm 22 of the angle head, and is supportedtherein in bearings 23 and 24. A beveled pinion 25 on the spindledrivingly engages a bevel gear member 26 of a combined nut running andnut crimping mechanism 27 housed in the angle head. The mechanism isshown as arranged in a second arm 28 of the angle head, which armextends at right angles to the longitudinal axis of the general housingof the tool.

The mechanism 27 has an initial first stage of operation uponapplication of torque to it by the spindle 21 in one direction to run awork nut 29 down to a predetermined degree of tightness; and it has asubsequent second stage of operation upon receiving torque from thespindle in an opposite direction to crimp the work nut.

The bevel gear member 26 of the mechanism 27 has a tubular body which issupported in a bearing 31 and has a splined driving connection 32 with asurrounding tubular body of a slidable dog 34. The splined connection 32allows axial movement of the dog relative to the gear member. The doghas a group of end jaws 35 which are drivingly engageable withcomplementary jaws 36 of a drive nut 37. A return spring 38 normallybiases the dog axially to a position wherein the jaws of the dog aredisengaged from those of the drive nut. One end of the spring abuts anoverhanging shoulder of the drive nut; and its other end is seated upona ring 39 having a bearing support upon an underlying shoulder of thedog.

A piston 41 having a tubular body sleeved upon the body of the dog ispneumatically operable in an expansible chamber 42 to slide the dogagainst the resistance of thespring into clutched driving engagementwiththe drive nut. A thrust ring bearing 43 is disposed between the pistonand an overlying shoulder of the dog. A passage 44 through the anglehead connects the expansible chamber with an external hose45 leading toa side port 46 of the housing. Port 46 connects with a chamber 47. Thelatter also connects with passage 16 leading to the motor; and issupplied with live air from the throttle valve 15.

The drive nut 37 has a tubular body, one end of which is journaled in abearing 48 seated in'an axial recess of a cap 49 that closes the rearend of the angle head. Bearing 48 is confined to the recess by means ofa retaining ring 51. The opposite end of the drive nut has bearingcontact with the upper end of the gear member 26; and a thrust ringbearing 52 is provided between the annular flange of the drive nut andthe overhead retaining ring 51. By means of this arrangement, the drivenut has rotation relative to the angle head and to the gear member butis curbed against relative axial movement.

The drive nut has an internal helical splined engagement with an upperscrew portion of the shaft of a travel wedge 54 (FIGS. 1 and Anintermediate smooth cylindrical portion ofthe shaft depends slidablythrough the body of the gear member 26. A lower shaft portion S5 oflarger diameter depends below the gear member and projects slidablythrough an axial opening of a gland ring 56 into the interior ofa jawholding sleeve 57. The gland ring is retained in a fixed position to thesleeve and serves as a closure to retain grease in the gear area above.Below the gland ring the shaft of the travel wedge terminates in a wedgehead 58 of larger diameter than its shaft portion 55.

The wedge head is splined to the holding sleeve for relative axialmovement as well as for rotatably driving the sleeve. To permit rotationof the sleeve, the latter is loosely supported at its upper end in theangle head between an overlying shoulder of the latter and an underlyingbeveled surface 59 of a sleeve screw 61. The

latter is entered into an open bottom 'end of the angle head. In thisarrangement, the holding sleeve 57 has rotation relative. to the anglehead but is restrained against relative axial movement. A lower end ofthe holding sleeve projects externally of the angle head.

The holding sleeve (FIGS. 1, 4, 7) has a group of six internallongitudinally extending spline tracks 62 spaced circumferentiallyequally apart. In each track is slidably received a separate one of sixradial splines 63 formed about the wedge head. Each spline has adownwardly and inwardly tapering flat angle surface 64 which terminatesin a tip 65 common to the several splines. The axis of the tip coincideswith that of the holding sleeve.

The wedge head normally has a raised position, as in FIGS. 1 and 7,under the bias of a return spring 66, in which position an annularshoulder at its top underlies the gland ring and an annular shoulder 60of its shaft portion abuts the gear member 26. Also, in this normalposition its common tip 65 is abutted slightly rearwardly of its apex bythe rounded vertex ends 67 of a group of crimping levers or jaw elements68.

There are six jaw elements, each located in a separate track 62 of theholding sleeve in underlying relation to the angle surface 64 of aseparate one of the splines of the wedge head. The jaw elements are ofageneral right triangular form. Each has a base end 69 and an upper tailportion having inner and back walls 71, 72 terminating in the vertex 67.The base end has a rounded back corner or heel 73 pivotally seated in aninside radius or pocket 74 formed adjacent the bottom end of 4 a relatedtrack of the holding sleeve; and the base end has a crimping toe or jaw75 atits inner end. The jaw 75 is flat faced and in extension of thewall 71. A shallow inside radius 75a (FIGS. 8a, 8b) separates the jawportion 75 from the upper portion of wall 71.

The several jaw elements are constantly urged by means of the load ofspring 66 acting through a jaw return plunger 76 to pivot their tail orvertex ends inwardly of the holding sleeve into abutment with the tip ofthe wedge head and to draw their jaw ends 75 outwardly to an opencondition as in FIGS. 1 and 7. The plunger has an elongated axial stem77 which is slidably received in an axial bore of the'wedge head. Thestem 77 terminates at its bottom in an inverted cup portion or head 78of enlarged diameter which has a bearing contact with the surroundinginternal wall of the wedge head. The cup portion has a radial annularlip 79 at its bottom, in the undersurface of which is a group of sixradial slots 81 (FIGS. 3, 7) spaced equally apart. In each slot isreceived a separate lug 82 projecting from below the mid-area of theinner face of a jaw element. The upper wall of each slot is pressedunder the load of the spring 66 upon the underlying lug 82 so as topivot the vertex end 67 of the related jaw element inwardly intoabutment with the tip of the wedge head as in FIGS. 1 and 7. The returnspring is under constant compression between opposed shoulders of thetravel wedge and the plunger.

In this normal position of the jaw elements, their six inner faces 71are in a substantially vertical position; and their jaws 75 define belowthe several lugs 82 a hexagonal opening for reception of a hex-form worknut 29, as appears in FIGS. 1 and 7. Accordingly, clockwise rotation ofthe jaw sleeve in this normal condition of the jaws will rotate and setthe work nut.

It can be seen that if the wedge head 58 is caused to move axiallydownward relative to the holding sleeve 57, its tip 65 and the anglesurfaces 64 of its several splines will ride in a camming action overthe vertexes 67 of the jaw elements causing the latter to pivot theirtail ends outwardly. The outward pivoting will cause the several flatfaced crimping jaws 75 to swing inwardly in an arc so as to close uponand forcefully compress or crimp corresponding flats of the work nut, asin FIG. 8. A slight inside radius 83 above the heel 73 of each jawelement is adapted in this outward pivoting action to seat over acomplementary radius 84 located above the pocket 74 so as to permit therear wall of the jaw to limit substantially upon the opposed back wallof the related track of the holding sleeve. This arrangement serves tomaintain a proper seated relation of the heel of the jaw to its' pocketduring pivoting of the jaw in a crimping direction.

It is to be noted in the crimping action that the jaw ends'75 of the jawelements move relative to the corresponding flats of the work nut 29 ina radially and upwardly curved path, each defining an are which isconcentric with its pivot. The flat face 75 of each jaw in penetrating acorresponding flat of the work-compressively displaces a triangularvolume of metal which flows inwardly to obtain a desirable lockedcondition of the nut and stud. When the jaws are withdrawn, a triangularindentation from which the metal was displaced appears in each flat. Thedeepest portion of the indentation is toward the work or lower end ofthe nut from where it extends angularly upward to intersect with theflat side of the nut. This manner of crimping the nut is of decidedadvantage in that it ensures that the jaws, as

well as the tool willbe readily released from the nut to slide the dog34 into driving engagement with the drive nut 37. Air also flows fromchamber 47 through passage 16 to the motor. Resultant rotation of themotor is transmitted through the bevel gearing 25, 26 and dog 34 toimpart clockwise rotation to the drive nut 37. The clockwise torque ofthe drive nut is transmitted through the helical splines to draw thetravel wedge 54 upwardly so as to frictionally lock its shoulder 60against the bevel gear 26. With this action, the bevel gear, dog, drivenut and travel wedge rotate as a unit and act through the wedge head 58to 'rotate the jaw holding sleeve 57 to cause the jaw elements 68 to rundown and set the work nut 29. When the work nut is driven to apredetermined degree of tightness, the resultant overload causes themotor to stall. The operator then manually shifts the reversing valve 17causing inlet air flow to shift its direction and drive the motor in anopposite direction. Consequent reverse rotation of the drive nut 37relative to the travel wedge 54 causes the latter to travel linearlydownward against the force of the return spring 66. In this movement,thewedge head 58 rides down the spline tracks 62 relative to the jawholding sleeve. At this time, the coned surface of the sleeve becomesloaded against the opposed mating surface 59 of the screw 61 so that thesleeve is restrained against rotation in a loosening direction of thenut. The downwardly moving wedge head cooperates with the several jawelements 68 to compressively and forcefully close their jaws upon andcrimp the work nut. Resistance offered by the jaw elements to furtherpivoting as their backs stop against the wall of the sleeve stalls themotor. The operator then releases the throttle valve to closedcondition, shutting off air flow to the motor. As the holding air actingin chamber 42 on the piston is then vented through the motor, spring 38disengages the dog 34. With this action, the drive nut 37 spins freelyabout as the travel wedge is linearly returned to normal by the plungerspring 66. Simultaneously with this action, the several jaw elements arepivoted under the spring load of the plunger 76 to normal open conditionas the wedge head restores upwardly. The tool is then lifted from thework; and the reversing valve 17 is manually reshifted to normalcondition preparatory to the next work operation.

Since crimping of the work nut occurs after a final torque has beendelivered to the work nut, marks left by the biting action of the jawends of the jaw elements into all six sides of the work nut provide apermanent indication that the required torque has been delivered. It isapparent that if the tool is used in setting a bolt having a hexagonalhead, it would serve not only in delivering a predetermined degree oftorque to the bolt, but it would also serve by means of the biting marksmade by the jaws in the bolt head to visibly indicate that the bolt headhas obtained the required torque. Accordingly, the tool is useable, notonly as a nut setting and crimping device, but also as a bolt settingand bolt marking device.

In place of the particular throttle valve 15 and reversing valve 17shown in FIG. 1, the handle section of the tool (as appears in FIG. 9)is shown as including a modified valving system, generally indicated at86, controlling flow of inlet air to the motor and to the angle headmechanism 27. The valving system functions automatically followingopening of a throttle valve member A to cause the tool to pass through acomplete cycle of setting and crimping the work nut and then restoringto normal condition without intervention of the operator.

The valving system includes the throttle valve A, a first slidablecontrol valve B, a reversing valve C, and a second slidable controlvalve D. An adjustable regulator valve E may be located between theinlet 87 and the throttle valve to vary the volume of inlet air flow tothe throttle valve.

Throttle valve A is designed so that after it has been manuallydepressed to open condition against the force of its return spring 88,it will remain pneumatically depressed until completion of the operatingcycle of the tool. It will then be restored automatically to closedcondition. I

The chamber 89 under the throttle valve A is con nected through ports90, 91, 92 (FIG. 12) and 93 to vent 94 (FIG. 14). When the throttlevalve is depressed to open condition, the pressure of supply airdeveloping over the upper area of the valve exceeds the force of itsreturn spring 88 so as to hold the valve in open condition, permittingremoval of the operator's hand from the. valve button 95.

Supply air flows through the open throttle valve to a common chamber 470from where it flows through side port 46a and the external hose 45 (FIG.10) to pressurize piston chamber 42 (FIG. 1) in the angle head. Thiscauses the piston 41 to force the dog 34 into driving engagement withthe drive nut 37, as earlier explained. Air also flows from the commonchamber 47a through port 96, chamber 97 of control valve B, and port 98to passages 99 and 100 (FIG. 12) to the motor feed ports 101 (FIG.causing the air motor 13 (FIG. 1) to operate in a nut tighteningdirection. The residual exhaust from the motor passes through ports 102,103 (FIG.

15), 104, 105 (FIG. 9), the chamber 106 underside of the second controlvalve C to the exhaust port 107.

. Supply air entering chamber 97 of thefirst control valve B passesthrough a check valved port 108 in valve B through port 109 at the topend of the valve and out of port 110 to port 111 connected with theupper chamber 112 of the reversing valve C. Chamber 113 at the bottom ofvalve C is connected through port 114 to passage 99 so that at this timevalve C is pneumatically balanced by live air in chambers 112 and 113 atits top and bottom.

When the work nut is tightened to 'a predetermined value of torque (asearlier explained) back pressure develops through motor feed passage 99into chamber 115 of valve B.'The effective area of valve B subject toair pressure is greater at its top end in chamber 115 since the stem end116 of the valve is exposed through a vent passage 117 to atmosphere.Accordingly, valve B is forced downward below port 96 by pressure inchamber 115 against the force of spring 120. This downward movementof'the valve closes supply port 96 to the motor feed passage 99 andopens it through chamber 115 and port 111 to chamber 112 at the top ofthe reversing valve C. The pressure air trapped in motor feed passage 99and in the connected chambers 97 and 113 below both valves B and Cexhausts through the motor. This action results in holding control valveB in its shifted. position and causes the reversing valve C to shiftdown against its return spring 119 below port 105 I Supply air is nowdirected from port 96 through the upper chamber 115 of control valve B,the upper chamber 112 of the reversing valve C, ports 105, 104 andpassage 103 (FIG. 15) to the feed ports 102 to drive the motor in anopposite direction to effect crimping of the work nut, as earlierexplained. The residual exhaust from the motor now'passes through theother set of motor feed ports 101 (FIG. 15), then ports 100, 99 (FIG.9), 114 and the intermediate chamber 106 of reversing valve C to theexhaust port 107. As the crimping action progresses, back pressure fromthe load on the motor progressively develops through port 104, port 120,lower chamber 121 of the second control valve D and through valvepassage 123 to chamber 124 at the top of valve D. When the jaws 68 stopagainst the wall of the sleeve in the crimping action, back pressure inchamber 124 develops to a value sufficient to shift valve D downwardagainst the force of its return spring 125. Shifting of valve D opens.port 126, permitting flow of supply air from ports 104, 120, 123, 126,93

(FIG. 14), 92 (FIG. 12) 91 and 90 (FIG. 9) to chamber- 4 89 at thebottom of the throttle valve A. Pressurization of chamber 89pneumatically balances the throttle valve, causing it to be restored toclosed condition by its return spring 88 and thereby stopping flow ofall air to the tool. The air trapped in the piston chamber 42 of theangle head then exhausts through the motor, as

earlier explained, permitting the mechanism 27 in the angle head torestore to normal.

What is claimed is:

1. In a nut running tool including a reversible rotary air motor,combined nut running and crimping mechanism for running down a work nutin response to rotation of the motor in one direction and for crimpingthe work nut in response to rotation of the motor in an oppositedirection, and means drivingly coupling the motor with the combined nutrunning and crimping mechanism. 1

2.- In a nut running tool as in claim 1, wherein control means isselectively operable for feeding operating air to the motor to drive itin a selected direction.

3. In a nut running tool as in claim 1, including control valve meansinitially manipulative to feed live air to the motor for driving it inthe one direction and being responsive to development of a predeterminedback pressure upstream of the motor to cause shifting of the live airflow to drive the motor in the opposite direction.

4. In a nut running tool as in claim 1, including control valve meansinitially manipulative to feed live air to the motor for driving it inthe one direction and being responsive to development of a predeterminedback pressure upstream of the motor to cause shifting of the live airflow to drive the motor in the opposite direction, and wherein thecontrol valve means is further responsive to development of apredetermined back pressure upstream of the motor during the time themotor is running in the said opposite direction to shut off flow of liveair flow to the motor.

5. In a nut running tool as in claim 1, wherein the combined nut runningand crimping mechanism comprises a rotatable open-ended sleeve member,pivotable camming jaws retained in the sleeve member, each having anelongated inner wall with a crimping toe at its bottom, the several jawshaving a normal pivoted position relative to the sleeve member in whichthe several inner walls are parallel to the. axis of the sleeve memberand define a multi-walled opening for reception of a work nut, and theseveral jaws being pivotable from this normal position to swing theupper ends of their inner walls outwardly relative to normal so as tocarry their toe ends arcuately inwardly of normal to effeet a crimpingaction upon a work nut received in the opening.

6. In a nut running tool as in claim 5, including a front end sectionhousing the nut running and crimping mechanism having an open front endin which the sleeve member is rotatably mounted, wherein a travel wedgemember of the nut running and crimping mechanism projects into a rearopen end of the sleeve member above the several jaws, the wedge memberhaving a splined driving connection with the sleeve member and beingaxially movable relative to both the sleeve member and the several jaws,the wedge member in its axial movement having camming cooperation withthe several jaws so as to pivot them from their normal position, andmeans connects the wedge member with the motor, the means havingresponse to rotation of the motor in said one direction to causerotation of the wedge member and as a consequence rotation of the sleevemember and having response to rotation of the 7. In a nut running toolas in claim 6, wherein a drive nut has in internal helical splineconnection with the travel wedge member, and a gear train drive connectsthe motor with the drive nut, the drive nut having rotation relative tothe travel wedge member and being restrained against relative axialmovement.

8. In a nut running tool as in claim 7, wherein pneumatically operableclutch means in interconnected in the gear train having a normalcondition disengaging the gear train drive from the drive nut.

9. In a nut running tool as in claim 8, wherein the clutch meansincludes a slidable dog having clutch jaws drivingly engageable withcomplementary jaws on the drive nut, a spring normally biases the dogout of clutched engagement with the drive nut, and a piston ispneumatically operable to slide the dog into clutched engagement withthe drive nut.

10. In a nut running tool as in claim 9, wherein means is provided forfeeding operating air concurrently to the motor and to the piston.

11. A combined n ut running and nut crimping tool comprising a housing,a fluid powered rotary motor within the housing, manipulative valvemeans controlling fluid flow to the motor selectively operable forcausing rotation of the motor in a forward or reverse direction, anangle head section defining a front end of the housing having an arm atan angle to the longitudinal axis of the tool, combined nut running andnut crimping mechanism incorporated in the arm of the angle headsection, gearing drivingly coupling the motor to the mechanism, themechanism being responsive to rotation of the motor in one direction torun down the work to a predetermined degree of tightness and beingresponsive to rotation of the motor in an opposite direction to squeezethe work.

12. A combined nut running and nut crimping tool comprising a housing, afluid powered rotary motor within the housing, an angle head sectiondefining a front end of the housing having an arm at an angle to thehousing, combined nut running and nut crimping mechanism incorporated inthe arm of the angle head section, gearing drivingly coupling the motorto the mechanism, the machanism being responsive to rotation of themotor in a particular direction to run down the work to a predetermineddegree of tightness and being responsive to rotation of the motor in anopposite direction to squeeze the work; and control valve meanscontrolling fluid flow to the motor, characterized by a throttle valveactuable to initiate fluid flow to the motor for rotation of the motorin a particular direction, by first valve means having response to apredetermined back pressure developing upstream of the motor to shiftthe direction of fluid flow to the motor to cause rotation of the motorin an' opposite direction, and by second valve means having response toa predetermined back pressure developing upstream of the motor while themotor is rotating in said opposite direction to cause shut-off of airflow to the motor.

1. In a nut running tool including a reversible rotary air motor,combined nut running and crimping mechanism for running down a work nutin response to rotation of the motor in one direction and for crimpingthe work nut in response to rotation of the motor in an oppositedirection, and means drivingly coupling the motor with the combined nutrunning and crimping mechanism.
 2. In a nut running tool as in claim 1,wherein control means is selectively operable for feeding operating airto the motor to drive it in a selected direction.
 3. In a nut runningtool as in claim 1, including control valve means initially manipulativeto feed live air to the motor for driving it in the one direction andbeing responsive to development of a predetermined back pressureupstream of the motor to cause shifting of the live air flow to drivethe motor in the opposite direction.
 4. In a nut running tool as inclaim 1, including control valve means initially manipulative to feedlive air to the motor for driving it in the one direction and beingresponsive to development of a predetermined back pressure upstream ofthe motor to cause shifting of the live air flow to drive the motor inthe opposite direction, and wherein the control valve means is furtherresponsive to development of a predetermined back pressure upstream ofthe motor during the time the motor is running in the said oppositedirection to shut off flow of live air flow to the motor.
 5. In a nutrunning tool as in claim 1, wherein the combined nut running andcrimping mechanism comprises a rotatable open-ended sleeve member,pivotable camming jaws retained in the sleeve member, each having anelongated inner wall with a crimping toe at its bottom, the several jawshaving a normal pivoted position relative to the sleeve member in whichthe several inner walls are parallel to the axis of the sleeve memberand define a multi-walled opening for reception of a work nut, and theseveral jaws being pivotable from this normal position to swing theupper ends of their inner walls outwardly relative to normal so as tocarry their toe ends arcuately inwardly of normal to effect a crimpingaction upon a work nut receIved in the opening.
 6. In a nut running toolas in claim 5, including a front end section housing the nut running andcrimping mechanism having an open front end in which the sleeve memberis rotatably mounted, wherein a travel wedge member of the nut runningand crimping mechanism projects into a rear open end of the sleevemember above the several jaws, the wedge member having a splined drivingconnection with the sleeve member and being axially movable relative toboth the sleeve member and the several jaws, the wedge member in itsaxial movement having camming cooperation with the several jaws so as topivot them from their normal position, and means connects the wedgemember with the motor, the means having response to rotation of themotor in said one direction to cause rotation of the wedge member and asa consequence rotation of the sleeve member and having response torotation of the motor in said opposite direction to cause said axialmovement of the wedge member.
 7. In a nut running tool as in claim 6,wherein a drive nut has in internal helical spline connection with thetravel wedge member, and a gear train drive connects the motor with thedrive nut, the drive nut having rotation relative to the travel wedgemember and being restrained against relative axial movement.
 8. In a nutrunning tool as in claim 7, wherein pneumatically operable clutch meansin interconnected in the gear train having a normal conditiondisengaging the gear train drive from the drive nut.
 9. In a nut runningtool as in claim 8, wherein the clutch means includes a slidable doghaving clutch jaws drivingly engageable with complementary jaws on thedrive nut, a spring normally biases the dog out of clutched engagementwith the drive nut, and a piston is pneumatically operable to slide thedog into clutched engagement with the drive nut.
 10. In a nut runningtool as in claim 9, wherein means is provided for feeding operating airconcurrently to the motor and to the piston.
 11. A combined nut runningand nut crimping tool comprising a housing, a fluid powered rotary motorwithin the housing, manipulative valve means controlling fluid flow tothe motor selectively operable for causing rotation of the motor in aforward or reverse direction, an angle head section defining a front endof the housing having an arm at an angle to the longitudinal axis of thetool, combined nut running and nut crimping mechanism incorporated inthe arm of the angle head section, gearing drivingly coupling the motorto the mechanism, the mechanism being responsive to rotation of themotor in one direction to run down the work to a predetermined degree oftightness and being responsive to rotation of the motor in an oppositedirection to squeeze the work.
 12. A combined nut running and nutcrimping tool comprising a housing, a fluid powered rotary motor withinthe housing, an angle head section defining a front end of the housinghaving an arm at an angle to the housing, combined nut running and nutcrimping mechanism incorporated in the arm of the angle head section,gearing drivingly coupling the motor to the mechanism, the machanismbeing responsive to rotation of the motor in a particular direction torun down the work to a predetermined degree of tightness and beingresponsive to rotation of the motor in an opposite direction to squeezethe work; and control valve means controlling fluid flow to the motor,characterized by a throttle valve actuable to initiate fluid flow to themotor for rotation of the motor in a particular direction, by firstvalve means having response to a predetermined back pressure developingupstream of the motor to shift the direction of fluid flow to the motorto cause rotation of the motor in an opposite direction, and by secondvalve means having response to a predetermined back pressure developingupstream of the motor while the motor is rotating in said oppositedirection to cause shut-off of air flow to the motor.